Power transmission



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I POWER TRANSMISSION Filed lay 12. 1945 1? Sheets- Sheet 1 i INVENTOR.

May 24, 1949.

E. ORSHANSKY, JR

POWER TRANSMI S SIGN 17 Sheets-Sheet 2 Fi 1ed May 12. 1945' IN VEN TOR.

flTTORNEYS May 24, 1949.

E. ORSHANSKY, JR

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Filed May 12, 1945 E. ORSHANSKY, JR

POWER TRANSMI SSION FIXED V01 V5 328 l7 Sheets-Sheet l3 INVENTOR 06cv mw ATTORNEYS E. ORSHANSKY, JR 2,471,117

POWER TRANSMISSION W 1"! Sheets-Sheet 14 May 24, 1949.

Filed May 12, 1945 Y E mroi ewrs May 24, 1949; E. ORSHANSKY, JR

POWER TRANSMISSIQN Filed May 12, 1945 17 Sheets-Sheet 15 ATTORN Y May 24, 1949.- E. ORSHANSKY, JR

POWER TRANSMISSION 17 Sheets-Sheet 16 Filed May 12, 1945 w NWN ATTORNEYS 7 May 24, 1949.

Filed May 12, 1945 E. ORSHANSKY, JR

POWER TRANSMISSION 172 45 T MOMENT 0F K m V: OPENING 0r MOMENT 0F use/mm; V9; V5 OPEN/N6 100% um 17 Sheets-Sheet 17 25% STIPUKE 10a man 25% smoms I NVENTOR HTTDRNEYS Patented May 24, 1949 .UNlTED STATES PATEN'l OFFlCE Elias Orshansky, In, Stamford, Com, assignor to The Acrotorque Company, Stamford, Conn., a corporation of Connecticut Application May 12, 1945, Serial No. 593,41!

1 35 Claims.

This invention relates to power transmissions, particularly to hydraulic transmissions of the variable speed ratio type, and has for its princi-. pal object to provide an improved transmission in which the losses ordinarily caused by elasticity of the liquid and of the associated mechanical elements are automatically eliminated, this being accomplished by causing the energy stored in the compressed liquid to be utilized in assisting the prime mover to drive the pistons.

This application is a continuatiOn-in-part of my application Serial Number 426,988, filed Jan- 4 uary 16, 1942, now abandoned.

According to .accepted mathematical analysis,

a detailed explanation of which is disclosed hereinafter, certain predetermined efllciencies should be achieved in operating transmissions of the type disclosed in my prior Patents 2,173,855 and 2,173,856 of September 26, 1939, 2,217,405 of October 15, 1940, 2,219,052 of October 22, 1940, and 2,-

first attributed to liquid leakage at the valves and pistons, in view of the employment of high pressures, but tests have indicated that despite elimination of valve and piston leakage the emciencies were still below the calculated values friction losses, of course, being taken into account.

losses closely paralleled those that would be expected to occur incident to liquid leakage, thus previously leading one to erroneously 'conclude that the losses were caused by leakage. However, since the leakage factor was substantially eliminated in the above tests, further tests were conducted to provide means, such as variations in valve timing, for preventing losses brought about by the above-described elasticity of the hydraulic system.

In analyzing the operating characteristics of a pump or motor cylinder and piston forming a part of a transmission, not only the volume of the displaced liquid but the volume of the liquid remaining in the cylinder, namely, the. undisplaced volume of liquid, must particularly be considered in order to correct for the above elasticity manifestations. For example, assuming a constant volume of liquid in the cylinder head, it can be readily seen that at maximum piston stroke the volume of liquid therein is at a minimum value, whereas, as the length of the piston 4 stroke is decreased from its maximum point to its minimum or substantially zero point, the volume of residual liquid within the cylinder increases to a maximum value at zero stroke. Correspondingly, as the residual liquid in the cylinder and cylinder head increases, the losses caused by the elasticity of the liquid, etc. increase and the efliciency of the pump or motor consequently decreases. It was thus discovered that for hydraulic units of the above type the greater the Furthermore, it has been found in transmissions of the above type embracing a pump-motor combination, each of which includes pistons reciprocating within cylinders, that the losses varied inversely with the length of the piston stroke, that is, the shorter the piston stroke the greater the loss and, consequently, the lower the efliciency therof. In fact, a point in the reduction of the piston stroke may be reached where no liquid can be transmitted, rotation of the output shaft thereupon ceasing, so that the efllciency becomes zero.

It has been discovered that the above losses are attributable substantially to the elasticity of the elements of the hydraulic system. By, the term elasticity" is meant the compressibility and expansibility 0f the liquid, as well as the compressibility and expansibility of'the component parts of the transmission, such as the cylinamount of undisplaced liquid within the cylinder and cylinder head the greater the losses and the greater is the correction required, 1. e., the greater the points of valve opening and/or closing must be adjusted from top and bottom positions of the pistons.

It is, therefore, an object of the invention to provide an improved transmission in which the hereinbefore-mentioned losses resulting from elasticity of the hydraulic system are substantially eliminated.

It is another object of the invention to provide an improved transmission of high efficiency.

It is yet another object of the invention to provide a transmission in which the mechanical connection between the driving and driven members is eliminated and in which a variable torque and speed drive results purely by the transmission of force from one member to the other through the medium of a liquid; a transmission of this type nevertheles embodying a structure such that substantially the entire energy will be delivered in the form of power to the driven member.

It is still another object of the invention to provide in an improved hydraulic unit of the displacement type an arrangement whereby the valve timing is varied in accordance with the hydraulic pressure.

It is a further object of the invention to provide in an improved hydraulic unit of the positive-displacement type an arrangement whereby the valve timing is varied in accordance with the length of the piston stroke.

It is a still further object of the invention to provide in an improved hydraulic unit of the positive-displacement type an arrangement whereby the valve timing is varied in accordance with the piston stroke and the hydraulic pressure of the system.

With the above objects in view, one aspect of the invention resides in a hydraulic displacement varying the opening and closing instants of the valve port.

Still another aspect of the invention resides in .a variable hydraulic pump unit of the positivedisplacement type wherein a working piston actuated by a variable stroke operating means (such as an adjustable eccentric) has associated therewith a composite valve timing means that is responsive both to the position of said variablestroke piston-operating means and to the pressure of the high pressure passage for automatically 'varying the opening and closin times of the valve port or ports.

Yet another aspect of the invention resides in such a device wherein a pair of valve means (bodies), connected in parallel, is employed for controlling the opening and closing instants of the working piston valve port or ports, said valve operating means being responsive to pressure changes and/or changes in the length of the working piston stroke.

A further aspect of the invention resides in a hydraulic pump unit of the positive-displacement type wherein a working piston has associated therewith a pair of composite single-acting valve piston structures adapted to respectively vary the intake and discharge port opening and closing instants in response to pressure in the high pressure passage and length of stroke of the working piston.

Still a further aspect resides in a pair of composite valve structures for a working piston wherein one pair of valve pistons, connected in parallel, is employed for controlling the opening and closing periods of the working piston cylinder intake port while the other pairof valve pistons. also connected in parallel, is employed for controlling the opening and closing periods of the working piston cylinder discharge port, said valve structures bein responsive to pressure changes and/or changes in the length of the piston stroke.

Yet a further aspect of the invention resides in a pair of composite valve structures for a working piston wherein the composite valves for the intake and discharge ports are independently responsive to the pressure variations of the high pressure passage and/or changes in the length of the piston stroke.

These and other aspects of the invention will be more fully described in the following specification taken in connection with the accompanying drawings in which:

Fig. 1A is a sectional side view of the forward portion of a transmission in which a fixed elasticity correction is employed;

Fig. 1B is a similar view of the rear portion of the transmission shown in Fig. 1A;

Figs. 2 and 3 are diagrammatic and exaggerated views of cams that may be employed for the control of the pump and motor of the transmission shown in Figs. 1A and 13;

Fig. 4 is a curve illustrating the elasticity by volume of the liquid as it is subjected to increasing pressure;

Fig. 5 is a curve illustrating the loss of efficiency of a transmission of the usual design operating at varying ratios of drive as well as at different pressures;

Fig. 6 is a diagram illustrating the correction that might be employed and factors which should be taken into account incident to the elasticity of the liquid and component parts resulting from the high-pressures developed in the pump;

Fig. 7 is a view similar to Fig. 6, but showing the factors involved in connection with the motor of the transmission;

Fig. 8 is a diagrammatic representation of a cylinder assembly of the pump and associated cams without elasticity correction;

Fig. 9 is a view similar to Fig. 8 except that the pump is provided with a fixed elasticity correction;

Fig. 10 is a view similar to Fig. 8 but illustrating a motor cylinder assembly without elasticity correction;

Fig. 11 is a view corresponding to Fig. 10 with the motor parts provided with a fixed elasticity correction;

Fig. 12 is a diagrammatic representation of a transmission similar to that shown in Figs. 1A and 1B, the pump and motor cylinder assemblies of which may be regarded as those shown in Figs. 8 to 11, inclusive;

Fig. 13 is a transverse sectional view taken along line I3I3 of Fig. 1B;

Fig. 14 is a fragmentary longitudinal sectional view showing the coupling structure employed in the transmission of Figs. 1A and 1B;

Fig. 15 is a view illustrating a transmission of the radial piston, pintle type;

Fig. 16 is a transverse sectional view taken along line |6--l6 of Fig. 15;

Figs. 17 to 20, inclusive, are diagrammatic transverse sectional views illustrating the valving structure embodied in the transmission of Fig. 15;

Figs. 21 and 22 are schematic views of pump and motor units, respectively, showing eccentrics .such as may be Wholly or partially employed in a unit of the type shown in Figs. 1A and 13;

Fig. 23 is a sectional side view of a pump in which the elasticity of the hydraulic system is automatically corrected for by means of a composite double-acting valve which is automatically responsive to change in pressure and length of piston stroke;

Fig. 24 is a transverse sectional view taken along line 2424 of Fig. 23 illustrating the working pistons and means for varying the piston stroke;

Fig. 25 is a sectional view taken along line 25-25 of Fig. 23 illustrating the fixed valve elements of the composite valve structure results in a change of volume.

Fig. 28 is a-partial plan view showing an arcuate slot and pin assembly adapted for varying the position of the eccentric associated with the varicomposite single-acting valves are associated with the working piston;

Fig. 37 is a view of the control linkage for the intake composite valve superposed upon a portion of the mechanism shown in Fig. '36;

Figs. 38 to 45, inclusive, are diagrammatic representations of the conditions existing in the pump unit of Fig. 36 for different percentages of load and stroke;

Figs. 46 to 48, inclusive, show curves illustrating the correction required at several percentages of stroke and load; and

Fig. 49 is a diagrammatic view of a cylinder head and piston for consideration-in connection with v the mathematical calculations.

In order to better illustrate the general effect of elasticity of tlie liquid and associated component parts upon the hydraulic system, the invention will be first analyzed from amathematical standpoint. From the following equations the elasticity losses that would normally exist in a hydraulic system may be calculated. Furthermore, the optimal valve timing for reducing the elasticity losses to zero may be determined from these equations. It is, of course, understood that the. equations can be applied'to any high pressure positive displacement pump unit irrespective of mechanical construction.

For the purpose of analysis; friction losses and such leakage losses as may occur have been neglected. It is to be noted that the term elasticity applies not only to the liquid employed but also to the component parts associated therewith, such as the cylinders, cylinder heads, pistons, connecting rods, cranks, shafts, etc., and, therefore, the following equations include the eflect of elasticity of these elements. Compression of'the liquid results in a greater quantity of liquid in the same volume and distortion of the pump parts In the following discussion the latter efiect will'be regarded as though it were caused by compressibility of the liquid and is included in the elasticity of the liquid.

For the sake of simplicity, the low or intake pressure has been considered as at atmospheric 7 pressure. However, the actual intake pressure may. instead be considered and accordingly the working pressure P will be the difference in pressure between the high and low pressure passages or manifolds.

Referring to Fig. 49 the following notations apply:

V,='designed displaced volume of pump cylinder,

in cubic inches.

C =designed undisplaced volume of pump cylinder assembly, in cubic inches. (Cylinder head and portion of cylinder, depending upon length of piston stroke, are included.)

V=V,+C,=total designed volumeoi pump cylinder assembly at atmospheric pressure, in cubic inches. I

E=volume change with change of pressure from atmospheric to P. in percent of original volume. (Includes deflection of parts.)

P=given pressure in pounds per square inch.

Vpi=Vn(1-E) =total volume of pump at pressure P, in cubic inches.

A =area of pump cylinder bore.

Sp=stroke of pump.

C=volume at atmospheric pressure in pump. (to

which oil will expand from volume Cp at working pressure).

Np=R. P. M. of pump.

Pump The total volume of the pump at pressure P in cubic inches is:

Vpl=Va-VuE The volume displaced by the piston in compressing oil to pressure P (and distorting the pump parts) =E (C'p-I-Vp) (1) The volume of oil discharged by the pump cylinder at pressure P =VpE(Cp+VD) (2) 'Work of pump The work required to compress oil from atmospheric pressure to pressure? P 5 The work required to discharge oil at pressure =[vp-E(c,+V,)1PN, (4)

Work done on the pump piston by an external source, assuming no work has been recovered:

The undisplaced volume or oil at the end 01.

the discharge stroke in the pump cylinder as-' sembly at pressure P =cp This volume Cp at pressure P has pent-up (potential) energy and will expand to atmospheric pressure, and may be used to force the pump piston downward. This expanded volume Thevolume of oil displaced during work on pump piston from pressure P to atmospheric pressure v This recoverable work may be returned to-the 

